Motion transmitting mechanism having planetary gearing



Nov. 27, 1962 M. B. KIRKPATRICK 3,0

MOTION TRANSMITTING MECHANISM HAVING PLANETARY GEARING Original Filed Aug. 8, 1955 5 Sheets-Sheet 1 EMWW Nov- 27, 19 M. a. KIRKPATRICK MOTION TRANSMITTING MECHANISM HAVING PLANETARY GEARING Original Filed Aug. 8, 1955 5 Sheets-Sheet 2 INVENTOR. /%x j zf/ferpar/r/m Nov. 27, 1962 M. B. KIRKPATRICK MOTION TRANSMITTING MECHANISM HAVING PLANETARY GEARING 5 Sheets-Sheet 3 Original Filed Aug. 8, 1955 INVENTOR. W51 ,fifienw/w/cz BY Iva/(wr Nov. 27, 196 M. B. KIRKPATRICK MOTION TRANSMITTING MECHANISM HAVING PLANETARY GEARING 5 Sheets-Sheet 4 Original Filed 'Aug. 8, 1955 INVENTOR. W41 J/fm'Aw'r/M Nov. 27, 1962 M. B. KIRKPATRICK MOTION TRANSMITTING MECHANISM HAVING PLANETARY GEARING 5 Sheets-Sheet 5 Original Filed Aug. 8, 1955 Stat This invention relates to motion transmitting mechanism and relates particularly to such mechanism having special planetary gearing and associated braking control.

The invention provides a transmission mechanism that has been found particularly useful in the selective rotation of different cutters in mining machines of the type disclosed and claimed in my copending application Serial No. 527,098, filed August 8, 1955, which has since matured into U.S. Letters Patent No. 2,864,600, dated December 16, 1958, and reissued as US. Letters Patent Reissue No. 24,965, and of which the present is a division.

The invention is shown in the accompanying drawings in a typical form such as is presently preferred by me. This particular form will be described in this specification, and the principles of this invention will be defined, both as related to the illustrated form and to equivalent forms and constructions, in the appended claims.

FIGURE 1 is a generally isometric and pictorial view illustrating a mining machine using the transmission mechanism of the invention to drive greater and lesser cutters.

FIGURE 2a is a simplified or diagrammatic isometric view, illustrating a portion of the driving or transmission mechanism, with parts all in idling relationship, and FIGURE 2b is an illustrative diagram showing the relationship of certain drive parts when they are operatively disconnected as shown in FIGURE 4b.

FIGURE 3a is a View similar to FIGURE 2a, and FIGURE 3b is a diagram similar to FIGURE 212, these FIGURES 3a and 3b illustrating the drive mechanism with parts in a drive relationship such as will effect rotation of the lesser cutter.

FIGURE 4 is a view similar to FIGURES 2a and 3a, showing the parts in a still further driving relationship, such as will effect rotation of the greater cutter, and FIGURE 5 is another similar view, showing parts in a still further driving relationship, such as will effect simultaneous counterrotation of both cutters.

FIGURE 6 is an axial sectional view through the machine with particular relation to details of the transmission, and FIGURE 7 is a transverse sectional view stepped back successively along the lines shown in FIG URE 6 at A, B, C and D, also illustrating details of the transmission.

It is believed that the invention will be understood most readily by, first, describing the principal components, and then describing its various capabilities and functions, concluding with a detailed description of the transmission mechanism and of the effect thereof on the operation of the machine.

The lesser cutter ring 1 is a short cylinder, or annulus, having cutter teeth 10a of suitable shape and material spaced at angular intervals about its periphery. In addition, there is an inner pilot annulus or stinger 11, also provided with cutter teeth 10b. These two annuli are connected together, as by the spokes 12, for conjoint rotation, and coal-breaking elements 12a, 11a and 11b are 3,9551551 Patented Nov 27, 1962 The greater cutter 2 is of appreciably larger diameter than the lesser cutter ring 1, and is supported from and for rotation with respect to a slightly smaller non-rotative cylindrical shell 3 of rather short axial extent. Like the lesser cutter l, the greater cutter 2 carries peripherally mounted cutter teeth 20 hingedly mounted at 20a to swing inwardly, and coal breaker elements 21a and 22a. It mounts also buckets 22 which rotate with the ring 2 and serve to lift material which has been broken loose and has fallen to the bottom of the bore, for depositing that material into a hopper 30, supported within the shell 3, so that it may pass out the rear end of the hopper, for discharge onto a suitable chute or conveyor indicated at C. A rotative feed screw 23 secured to the greater cutter 2 for rotation with the latter serves to advance the material rearwardly through the shell 3.

The lesser cutter ring 1 is preferably mounted .at one end of a reciprocable and axially movable hollow plunger rod 13, which receives Within its opposite end a fixed plunger head or piston 31. The plunger rod 13 is also rotatable, and the means for rotating the same will be described later. It will be understood that the application of pressure fluid at one side or the other of the plunger head 31 will efiect projection or retraction of the plunger rod 13 and of the lesser cutter which it carries at its outer end.

Distributed about the shell 3, closely behind the greater cutter ring 2, are several inflatable pads 32, faced with metal shoes as skids. The lowermost pad 32 serves as a support for the machine as a whole. If all such pads 32, 32a are expanded with maximum force radially against the wall of the bore they will grip with sufiicient force that the machine cannot be displaced axially nor rotationally. While they are so expanded they constitute reaction points whence the rotating lesser cutter 1 may be pushed forwardly, cutting its way ahead of the greater cutter 2, which at such a time would be non-rotative. By expanding the lower pad 32a only sufficiently to support the weight of the machine, and the remaining pads 32 less than is required for gripping, they accomplish the very important functions of steadying and guiding the greater cutter 2, close behind the latter, as the latter rotates and .advances. They function similarly to the wellknown catspaws of cylinder-boring machines, whether the cutter 2 be rotated alone or conjointly with the cutter 1. It is this close-up guidance that avoids chattering and vibration, and leaves a smooth, machined bore.

The lesser cutter 1 also has an inflatable ring 14, close behind its teeth Elia, but this functions primarily as an anchorage means. After the lesser cutter has been projected forwardly, while rotating, cutting a bore to the desired axial extent beyond the. non-advancing, nonrotative greater cutter 2, rotation of the cutter 1 ceases and the ring 14 is inflated sufiiciently that it grips its bore wall to serve as a reaction point whence the greater cutter 2, now rotative, can be dragged ahead. As the greater cutter advances it cuts its way into the vein, and enlarges the bore. This push-drag procedure can be repeated, but ordinarily is used only to start a bore, and advance is usually accomplished by effecting simultaneous counterrotation of the cutters 1 and 2, at like peripheral speeds, while advancing the machine axially by traction means 33. Outboard wheels 34 effect guidance only, and are not depended upon to resist'vibration.

Wheels 33, controlled by r-ams 334 are primarily for traction by means of the motor 33b, either when the machine is not entered within a bore, or while it is being advanced within a bore during simultaneous counterrotation, or while it is being backed from a bore. Advance of the machine by the push-drag procedure of first pushing the lesser cutter ahead, then anchoring the latter and dragging ahead the greater cutter is normally shell 3 and greater cutter 2.

Assuming the machine to be about to commence a new 'bore, the shell 3 is suitably anchored or hacked, and the lesser cutter 1 is pushed ahead by thrusting on the plunger rod 13, while rotating; the greater cutter 2 is held stationary. The cutter 1 cuts its way into the vein V, until it has advanced as far as is practicable. When the lesser cutter 1 has advanced as far as is practicable the ring 14 is expanded with sufiicient force to grip the bore wall, and rotation of the lesser cutter 1 is stopped by disengaging it from its drive, through transmission'mechanism still to be described. Through the transmission the greater cutter 2 is rotated. By reaction from the now-anchored lesser cutter 1, through the hollow plunger rod 13, the rotating greater cutter 2 an the sheel 3 are dragged ahead. The pads 32 and 32a act as steadying guides close behind the greater cutter '2. and prevent vibration. When advance of the greater cutter has proceeded as'far as is practicable, the original status is restored, and the lesser cutter may resume its advance, reacting from the pads 32 and 32a, or the normal mode of operation may commence, in which both cutters 1 and 2 rotate simultaneously but oppositely, advance being effected by the Wheel 33 and motor 33b.

The drive for rotating the cutters 1 and 2 is from one or several motors M, which may be electric or hydraulic in character. Electric motors are shown. If there be several such motors, and this is preferred because of the limitations of space, they would be connected by individual or common driving chains 40 to a common drive sprocket wheel 4. This sprocket wheel 4 is mounted by a bearing 4a to rotate about a rotative sleeve 19, which in turn is journalled at 37a and 37b within the forward end and the rear cover 37c of a transmission casing 37 which is fixed with relation to the stationary shell 3. The internal hollow plunger rod 13 is keyed at 13a to slide axially with relation to the ro tative sleeve 19, and the latter is, in turn, keyed to a sun gear 18 which is the immediate means for driving the lesser cutter 1. The greater cutter 2 is supported upon the outer end of a rotative sleeve 29, which is keyed at its rear end to the sun gear 28, by which the larger cutter is caused to rotate. The whole is journalled within the transmission casing 37.

It will be noted that the two sun gears 18 and 28 are at opposite faces of the main driving sprocket wheel 4. Associated with the sun gear 18 is a coaxial idler gear 17 slightly larger in diameter than the sun gear 18, and the two are interconnected by integral planet gears 17a and 18a (of which there are several sets distributed angularly about the sprocket wheel 4) rotative about a common stub shaft 41 which is fixed with relation to and rotative with the driving sprocket wheel 4. A similar idler gear 27 coaxial with the sun gear 28, and integral connecting planet gears 27a and 28:: on the opposite end of the same stub shaft 41, complete the connection between the gears 28 and 27. The gear 27 in this instance is somewhat smaller than the sun gear 28, and the gears 17 and 27 are of like diameter.

A brake drum 42 is fast to the gear 17 and a brake drum 43 is fast to the gear 27. By application of spiral brake bands 44 and 45 to the respective drums 42 and 43,, the rotation of the gear 17 or of the gear 27 can be stopped. Stoppage of gear 17 effects rotation of the complemental driving gear 18, and of the lesser cutter 1, while stoppage of gear 27 effects rotation of the gear 28 and of the greater cutter 2. A third brake drum- 47,.keyed-to an. extension 19a of the rotative sleeve 19, can be stopped by application of expanding brake shoes lesser cutter 1.

'46, which halts rotation of the lesser cutter 1. The application of these several braking means i under control of an operator such as would ordinarily occupy the seat S at the rear end of the machine, and who has his operating handles H and H conveniently in front of him.

Before describing the detailed operation of the transmission mechanism thus described in general, it should be noted that the flexible conduit 15, previously mentioned, extends through the plunger means from a connection at 15a to a pressure fluid source, and at its outer end to the distensible or inflatable ring 14 of the The connections of 31a and 31b are for application of fluid under pressure to force the plunger rod 13 inwardly, acting on the annular pressure head 31c, or outwardly, acting on the plunger head 31, in the axial direction. Other pressure fluid connections, not shown, will accomplish the distension and permit retraction of the pads 32 conjointly, and of the pad 32a alone, all of which are on the non-rotative shell 2. Valves and valve handles H to control these are also under control of the operator at his station.

It will now be in order to describe in detail the operation, under varying conditions, of the transmission mechamsm.

It will be noted that all three brakes 42, 44; 43, 45 and 46, 47 are relased. The main sprocket wheel 4 is rotative, hence, the planet gears 17a, 18a and 27a, 28a revolve about the idler gears 17 and the corresponding sun gear 18, and the idler gear 27 and the corresponding sun gear 28. It being assumed that the cutters 1 and 2 are entered within their respective portions of a bore, the sun gears 18 and 28 are held stationary against the resistance of the material with which they are engaged; this holds the gears 18' and 28 stationary. Through theplanet gears, the idler gears 17 and 27, respectively, merely rotate idly, since the corresponding brakes are off. No external movement occurs. It would be feasible, of course, to apply the brake at 46, 47, and no harm would result.

The principle of operation with parts in this operative relationship is illustrated in FIGURE 2b, wherein the coaxial idler and sun gears 17 and 18 of different diameter are straightened out as though they were racks. If we assume that the sun gear 18 is held against rotation, as it is in fact by the resistance of the working face to rotation of the lesser cutter ring 1, and then roll the planet gears 17a, 18a along these fixed racks through 360 of the gears 17a, 18a, the gear 18a will have advanced a distance along the rack 18 equal to 11' times the pitch diameter of 18a. The gear 17a, being integral with the gear 18a, will have advanced along its rack 17 by an identical distance. The distance along the rack 17 necessary for a 360 rotation of gear 17a is, however, shorter than the distance 18a advances along its rack 18 during 360 of rotation, by the distance (difference) 170. In order that 17a can keep up with 18a, with which it is integral, the rack 17 must advance through the distance 170. Since the idler gear'1-7 is not braked under the assumed conditions (see FIGURE 2a), this idler gear 17 rotates with respect to its sun gear 18, in accordance with arrow 17b. The idler gear 17 being free of positive connection to the sprocket wheel 4, the lesser cutter 1 does not rotate. The same situation holds true as to the rotation about the gear 2 8, which is held immovable by the resistance applied externally to the greater cutter 2. Revolutionof planet gears 27a, 28a effects rotation of the idler gear 27, but since the brake at 43, 45 is released, the parts merely rotate idly within the transmission, and no external movement is effected.

FIGURE 3a illustrates the relationship of parts when the lesser cutter 1 alone is rotating. In this view the brake band 44 is applied to the brake drum 42, stopping rotation of the idler gear 17. As the main sprocket wheel 4 continues to rotate the planet gears 17a, 18a and 27a, 28a continue to revolve with the sprocket wheel 4.

Since the brake drum 45 is released from the brake drum 43 and the resistance of the greater cutter 2 to rotation holds the gear 28 against rotation, as in the case of FIGURE 2a, the gear 27 and the brake drum 43 continue to rotate as before, as indicated by the arrow 27b, but since the brake shoe 46 is released from the brake drum 47, the hollow plunger rod 13 and the lesser cutter 1 at its outer end are free to rotate, the brake 42, 44 halts rotation of the idler gear 17, hence, the continued revolution of the planet gears 17a and 18a effects rotation of the sun gear 18 in the sense indicated by the arrow 13b. Since the latter is, in effect, integral with the hollow plunger rod 13, the latter is caused to rotate in the direction indicated by the arrow 13b, effecting rotation of the lesser cutter 1, as at In. Again this is understandable by reference to FIGURE 3b. Rolling the planet gears 17a and 18a through 360 along their racks 1'7 and 18 respectively, but now with the rack 17 held (by application of the brake at 42, 44) against rotation, obviously the lesser distance of 1r times the diameter of 17a as compared to 1r times the diameter of 18a will exert a thrust on the rack 18, tending to displace it in the direction and by the amount indicated at 18b in FIGURE 3b. The gear 18 tendsto rotate as shown at 18b in FIGURE 3a, and since the lesser cutter 1 is in effect fast to 18, this lesser cutter iscaused to rotate against the reaction of the brake at 42, 44.

By proper application of the correctly selected brake drum and by virtue of the relationship as to siZe of the idler gear 17 and sun gear 18 and of the connected integral planet gears 17a and 18a, it is seen above that rotation of the single lesser cutter 1, while the greater cutter 2 is stationary, is accomplished, and by expanding the pads 32 tightly during this time and deflating the ring 14 sufficiently that it will steady but not bind, and thrusting axially forward the plunger rod 13, the lesser cutter 1 cuts as it rotates and advances, reacting from the grip afforded by the pads 32 on the exterior of the bore which has been cut by the greater cutter 2.

Coming now to FIGURE 4, this illustrates the situation wherein the lesser cutter 1 has advanced as far as it is desired to advance it for the time being, and is held stationary by the expansion of the ring 14. The pads 32 have now been deflated sufficiently that they steady but do not bind, and the greater cutter 2 is rotating in the sense indicated by the arrow 2a which, it will be noted by comparison with FIGURE 3a, is counter to the sense of rotation 1a for the cutter 1 in the latter figure.

To accomplish the rotation 2a in FIGURE 4, the stillrotation sprocket wheel 4 is connected to the sun gear 28, the brakes 43, 45 and 46, 4'7 are engaged, as indicated in FIGURE 4, but the brake 42, 44 is released. Release of the brake 42, '44 enables the idler gear 17 to rotate idly, reacting from the gear 18, which is held against rotation by the external reaction applied to the lesser cutter 1, but the revolution of the planet gears 27a and 23a. effects a reaction from the now-stationary idler gear 27, held by the applied brake 43, 45, to effect rotation of the gear 28 by reaction from the now-stationary gear 27. Rotation of the gear 28 is effected in the rotative sense indicated as 23b in FIGURE 4, consequently, the sleeve 29 is rotated in the sense indicated by the arrow 2%, and effects rotation of the greater cutter 2 in the sense indicated by the arrow 2a. A diagram similar to FIGURES 2b or 3b could be drawn to indicate how this is accomplished, but the principle has been indicated in the diagrams in FIGURES 2a and 3b, and it is believed to be unnecssary in connection with FIGURES 4 and 5.

In FIGURE 4, then, the lesser cutter 1 having been advanced to the limit of its desired axial advance for the time being, and being held non-rotative by tight expansion of the ring 14, the greater cutter 2 is rotated and meanwhile is being advanced by aplication of pressure to the proper side of the plunger 31, to effect axial advance of the greater cutter 2 While it is rotating, by reaction from the lesser cutter 1 and its expanded ring 14.

FIGURE 5 indicates the condition which would apply when both cutters are rotated simultaneously and in rotative senses counter to one another. (This is the preferred mode of operation.) In this instance, the machine is advanced as a whole by energization of the motor 33b applied to the lower wheel 33, or to the several wheels 33.

The sprocket wheel 4 continues to rotate as before and in the same sense. Brakes 42, 44 and 43, 45 are both applied, but the'brake 46, 47 is released. It follows that the idler gears 17 and 27 are fixed with relation to the shell 3, the ring 14 is deflated, the pads 32 are deflated, SUfilClCIlily that they do not bind, although they continue to steady the machine, and pad 32a to support it, and both cutters 1 and 2 are free to rotate.

Revolution of the planet gears 17a and 18a effects a reaction from the brake-held, now-stationary idler gear 17 to effect rotation of the coaxial gear 18 in the sense 181). In similar fashion, revolution of the planet gears 27a and 28a effects a reaction from the brake-held, now-stationary idler gear 27 to effect rotation of the gear 28 in the sense indicated by the arrow 28b. The gear 18 is connected to rotate the lesser cutter 1 in the sense indicated at 1a, while rotation of the gear 28 effects rotation of the greater cutter 2 in the sense indicated at 2a, which is counter to the sense 1a.

By proper choice of gear relationships, the rapidity of rotation of the greater cutter 2 in the sense 2a can be somewhat less than the rapidity of rotation of the lesser cutter 1 in the sense 1a, so that, in effect, the torques produced by the two cutters 1 and 2 are counter and generally equal, and the circumferential rate of cutting may be made equal. In this manner, the two cutters 1 and 2 neutralize each other, consequently, there is no need for provision to otherwise neutralize the torque. The machine as a 'whole is readily advanced along the bore by the motor 33b; meanwhile the cutters cut their Way into the bore, the loosened material being deposited within the hopper 30 by means of the buckets 22 and so being removed at the rear end of the hopper 30 by means of the chute C or other convenient means.

The invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiment is therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein.

What is claimed and desired to be secured by United States Letters Patent is:

1. Transmission mechanism for rotating either or both of coaxial inner and outer members, comprising two sun gears each fixed for rotation with its respective one of said members, idler gears coaxial with and respectively adjacent each sun gear, a drive wheel rotatably supported on one of said members coaxial with the sun and idler gears, two pairs of conjointly rotative and operatively connected planet pinion gears mounted upon and revoluble with the drive wheel, the individual pinions of one pair intermeshing with the sun gear and idler gear, respectively, of the inner member, and the individual pinions of the other pair intermeshing with the sun gear and idler gear, respectively, of the outer member, brake means selectively applicable to halt rotation of either idler gear, and further brake means applicable to halt rotation of the inner member.

2. A transmission mechanism as in claim 1, wherein said outer member is tubular and extends in telescoping relation over said inner member, and said drive wheel is mounted on said inner member.

3. Motion transmitting mechanism comprising a rotatable power transmitting member, two power transmitting shafts, one being hollow and the other extending therethrough, coaxial rotatable sun gears fixed on the respective shafts adjacent said member, a rotatable idler gear rotatably mounted on each said shaft coaxial with said sun gears, means rotatably supporting said member on one of said shafts, a system of planet gearing carried by said member and interconnecting each sun gear With its associated idler gear and brake means for selectively arresting rotation of either idler gear.

4. Motion transmitting mechanism comprising a support, two coaxial shafts rotatably mounted on said support, a rotatable power transmitting member rotatably supported on one of said shafts, sun gears coaxial with said member and rigidly mounted on the respective shafts at opposite sides of said member, idler gears rotatably mounted on the respective shafts adjacent each sun gear, a plurality of compound planet gears rotatably mounted on said member and interposed between and meshed with each sun gear and its associated idler gear and means for selectively braking rotation of either idler gear.

5. Motion transmitting mechanism comprising a support, two coaxial shafts rotatably mounted on said support, one of said shafts being hollow and the other extending therethrough, a rotatable power transmitting rotatably mounted on the respective shafts at opposite sides of said member coaxial with said member, idler gears rotatably mounted on the respective shafts coaxially of said sun gears, a first planet gearing connecting one of said sun gears with its associated idler gear comprising a first plurality of compound gears journalled on said member and each compound gear having one gear member journalled on the inner of said shafts, sun gears section meshed with said one sun gear and another gear section meshed with the associated idler gear, a second planet gearing interconnecting the other sun gear with its associated idler comprising a second plurality of compound gears journalled onsaid' member and each compound gear having one gear section meshed with said other sun gear and another gear section meshed with the associated idler gear and means for selectively braking each of said idler gears.

6. In the motion transmitting mechanism defined in claim 5, the compound planet gears of the first plurality being coaxial with compound gears of the second plurality.

7. In the motion transmitting mechanism defined in claim 6, said coaxial compound gears being rotatably mounted on a common shaft rigid with said rotatable power transmitting member.

8. In a power transmission, a support, two coaxial power output members rotatably mounted on said support, a power input member, bearing means supporting said input member on one of said output members adjacent one end of the other output member, two sun gears, one rigid with each output member and disposed on opposite sides of the input member, idler gears journalled on the output members adjacent the sun gears, compound planet gears mounted on the input member and operably connecting the respective sun and idler gears, brake means for selectively arresting the idler gears, and a bearinginterposed between the other ends of said output members.

References Cited in the file of this patent UNITED STATES PATENTS 1,465,796 Twomley Aug. 21, 1923 2,737,828 Seybold Mar. 13, 1956 v FOREIGN PATENTS 674,580 France Oct. 22, 1929 369,561 Italy Mar. 24, 1939 UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No, 3,065 65l November 27, 1962 Max B. Kirkpatrick It is hereby certified that error appears in the above numbered patent requiring correction and that the said Letters Patent should read as corrected below.

Column 3, line 22, for "sheel" read shell column 4 line 27, for "relased" read released column 7, line 32, strike out "member journalled on the inner of said shafts, sun gears".

Signed and sealed this 12th day of November 1963.

(SEAL) Attest:

ERNEST W. SWIDER EDWIN L. REYNOLDS AC g Commissioner of Patents Attesting Officer 

